US4711094A - Reverse cycle heat reclaim coil and subcooling method - Google Patents

Reverse cycle heat reclaim coil and subcooling method Download PDF

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Publication number
US4711094A
US4711094A US06/929,422 US92942286A US4711094A US 4711094 A US4711094 A US 4711094A US 92942286 A US92942286 A US 92942286A US 4711094 A US4711094 A US 4711094A
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United States
Prior art keywords
coil
condenser
subcooling
refrigerant
heat
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Expired - Fee Related
Application number
US06/929,422
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English (en)
Inventor
Roland A. Ares
Robert A. Jones
Norman E. Street
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Hussmann Corp
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Hussmann Corp
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Assigned to HUSSMANN CORPORATION, A CORP. OF DE. reassignment HUSSMANN CORPORATION, A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ARES, ROLAND A., JONES, ROBERT A., STREET, NORMAN E.
Priority to US06/929,422 priority Critical patent/US4711094A/en
Priority to CA000548148A priority patent/CA1274094A/fr
Priority to DE19873735808 priority patent/DE3735808A1/de
Priority to GB8724996A priority patent/GB2198828B/en
Priority to JP62285138A priority patent/JPS63140259A/ja
Priority to AU81118/87A priority patent/AU583246B2/en
Priority to SE8704402A priority patent/SE8704402L/
Publication of US4711094A publication Critical patent/US4711094A/en
Application granted granted Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/22—Refrigeration systems for supermarkets

Definitions

  • the invention relates generally to the commercial and industrial refrigeration art, and more particularly to reverse cycle condensers for such refrigeration systems.
  • the invention is embodied in a refrigeration system having a heat reclaim coil with first valve means selectively connecting the coil between the compressor and condenser means in a heat reclamation mode during winter operation, and second valve means selectively connecting the coil between the condenser means and a system receiver in a subcooling mode during summer operation.
  • the invention further includes the method of effecting reverse cycle operation of the heat reclaim coil in its seasonal heat reclamation and subcooling modes.
  • the principal object of the present invention is to provide a refrigeration system that will maintain yearround deep subcooling of liquid refrigerant without the use of mechanical subcoolers.
  • Another object is to provide more efficient air conditioning reheat for humidity control during summer operation.
  • Another object is to employ a heat reclaim coil in a reverse cycle subcooling and sensible reheat mode for beneficial air conditioning comfort and improved refrigeration performance.
  • Still another object is to provide a compensation factor in the refrigerant overcharge typically associated with low head pressure operation of compressors and volumetric expansion during warmer seasonal operation.
  • FIG. 1 is a diagrammatic view of a typical refrigeration system embodying the invention, and illustrating a moderate season operational mode
  • FIG. 2 is a diagrammatic view illustrating a summer operational mode of the invention.
  • FIG. 3 is a diagrammatic view illustrating a winter operational mode of the invention.
  • a closed refrigeration system embodying the invention is illustrated as being of the commercial multiplexed type having dual or twin parallel compressors as installed in a supermarket food store for operating a plurality of separate fixtures, such as refrigerated storage and display cases, but it will be understood by those skilled in the art that such a system may be adapted to other commercial or industrial installations.
  • the term "high side” is used herein in a conventional refrigeration sense to mean the portion of the system from the compressor discharge to the evaporator expansion valves and the term “low side” means the portion of the system from the expansion valves to the compressor suction.
  • the refrigeration system includes a pair of compressors 10 and 11 connected in parallel and each having a suction or low pressure side 12 operating at a predetermined suction pressure and a discharge or high pressure side 13 connected to a common discharge header 14 through which hot compressed gaseous refrigerant is discharged for condensing.
  • the discharge header 14 is connected through a reversing valve 15 in discharge line 16 to a condenser 17 having split coil sections 18 and 19 and conventionally being mounted outside on the roof R of the building.
  • the condenser coil section 18 is connected to the compressor discharge line 16 by an inlet branch line 18a and to a refrigerant outflow conduit 20 by a branch outlet line 18b.
  • the condenser coil section 19 is connected to the discharge line 16 by a branch inlet line 19a and to the outlet conduit 20 by branch outlet line 19b.
  • the refrigerant is reduced to its condensing temperature and pressure by ambient air flow through the condenser 17, and the outlet conduit 20 is connected through a four-way reversing valve 21 and condensate line 22 to a receiver 23 forming a liquid refrigerant source for operating the system.
  • a flooding valve 24 may be provided in the conduit 22 in a typical manner to produce variable condenser flooding and maintain compressor head pressures at or above a preselected minimum as during winter or cold weather operation.
  • the receiver 23 may be of the surge-type or flow-through and is connected to a liquid header 25 for conducting liquid refrigerant to branch liquid lines or conduits 26 leading to evaporator coils 27, 28 and 29 associated with different refrigerated fixtures (not shown) and being representative of numerous evaporators that may be connected into the refrigerant system.
  • the inlet of each evaporator 27, 28 and 29 is controlled by an expansion valve 30 which meters refrigerant into the evaporators in a conventional manner.
  • the outlets of the evaporators are connected through branch suction lines or conduits 31 to a suction header 32 connected to the suction side 12 of the compressors 10 and 11 and through which vaporous refrigerant from the evaporators is returned to the compressors to complete the basic refrigeration cycle.
  • the fixture evaporators may be selectively defrosted as periodically required in a typical way, as by electric or hot gas defrost.
  • the construction and operation of the system so far described will be more fully understood by reference to U.S. Pat. Nos. 3,427,819 and 4,522,037.
  • the invention is embodied in a heat reclaim coil 35 that is selectively connected into the refrigeration system to function in reverse cycle in a winter heat reclamation mode and a summer subcooling and reheat mode.
  • the heat reclaim coil 35 is located in an air handler unit 36 positioned in air flow communication with a building room or store space S to be heated or cooled.
  • Such an air handler unit 36 is disclosed in U.S. Pat. No.
  • a ducted airway 37 having an air inlet and sequentially arranged components including an air filter 38, a push-through fan or blower 39, an air conditioning coil 40 that is part of a separate air conditioning system or heat pump (not shown), the heat reclaim coil 35 and a supplemental space air heater 41.
  • the heat reclaim coil 35 has piping connections 42 and 43 on opposite sides thereof, the first piping connection 42 being connected by conduit 44 to the reversing valve 15.
  • a one-way check valve 45 is provided in conduit 44 to permit refrigerant flow only from the valve 15 to the heat reclaim coil 35.
  • the second piping connection 43 is connected to a conduit 46, which connects at a tee 47 to another conduit 48 in turn connected into branch inlet line 19a at another tee 49 leading to one of the condenser coil sections 19.
  • a one-way check valve 50 is provided in conduit 48 to limit refrigerant flow therein only in the direction of the condenser section 19 and prevent reverse flow.
  • a one-way check valve 51 is also provided in branch conduit 19a upstream of the tee connection 49 to limit refrigerant flow in conduit 19a only in the direction of the condenser section 19.
  • the valve 15 will be operated by a store thermostat 52 sensing the temperature of the room air to connect the discharge header 14 to the conduit 44 so hot compressed refrigerant will be circulated through the heat reclaim coil 35 to heat room supply air recirculated through the air handler 36 by fan 39.
  • the temperature of the refrigerant is reduced to a point just above saturation and the refrigerant then flows through conduits 46, 48 and 19a to the condenser section 19 in which the refrigerant is fully condensed and deep subcooling is inherently achieved in winter operation.
  • Subcooled refrigerant condensate flows from the condenser section 19 through conduits 19b and 20 to the second reversing valve 21, which connects to condensate line 22 and the receiver 23 during winter and moderate weather operations.
  • the outlet branch conduit 18 b from the condenser section 18 has a one-way check valve 53 to prevent backflow of condensed refrigerant into this section during winter operations.
  • the one-way check valves 45, 51 and 53 may be of well-known conventional construction, either a swing check element (not shown) normally closing by gravity or a spring-loaded element (not shown) normally closed under spring pressure of negligible force, which open under refrigerant flow pressure in one direction only.
  • the check valve 50 is preferably of the spring-loaded type having a force of about 2-5 psi, and which is normally kept closed in summer operation by the additional force of the high side pressure drop in the magnitude of 2-10 psi across the condenser section 19.
  • the check valve 50 is capable of opening in summer operation under unusual refrigerant surge conditions in cycling compressors or the like to relieve any refrigerant hydrostatic condition developing within the coil 35 and provide pressure equalization to prevent hammering.
  • the reversing valve 15 is ported to connect the line 16 to a bleeder line 54 during the heat reclaim mode when the compressor discharge is diverted to the heat reclaim coil 35.
  • the bleeder line 54 is connected to the suction side 12 of one of the compressors (10, 11) or to the suction header 32 thereto, and a capillary tube 55 is provided to assure that the refrigerant bled down from condenser section 18 through line 16 will undergo a change of phase to vapor when going to the compressor suction.
  • a capillary tube 55 is provided to assure that the refrigerant bled down from condenser section 18 through line 16 will undergo a change of phase to vapor when going to the compressor suction.
  • FIGS. 1 and 2 the heat reclaim coil 35 is reversely connected in the system for summer operations.
  • a conduit 58 connects the tee 47 (conduits 46, 48) with another port of the reversing valve 21 to provide an open piping connection to one side of the heat reclaim coil 35, and the other side of this coil 35 has another conduit 59 extending between the conduit 44 on the downstream side of check valve 45 and a fourth port in the reversing valve 21.
  • FIG. 1 illustrates the valve 21 in position for normal moderate weather operation in which the condensate outflow from the condenser 17 through conduit 20 is diverted directly into the line 22 and receiver 23. In the summer mode shown in FIG.
  • the reversing valve 21 is turned to divert condensate outflow from the conduit 20 into the conduit 58 in a reverse flow path through the heat reclaim coil 35 and back through conduits 44, 59 to the reversing valve 21 and thence to condensate line 22 and the receiver 23.
  • Another conduit 60 is provided between the heat reclaim coil 35 and the suction header 32 to provide bleed-down of residual refrigerant from the heat reclaim coil 35 during inoperative (moderate weather) periods.
  • the conduit 60 is shown connected to conduit 59 and is controlled by a normally closed solenoid valve 61, although the conduit 60 may be connected at any place that will provide gravity refrigerant flow to the suction side 12 of the compressor means 10, 11.
  • the heat reclaim coil 35 does not fully reduce refrigerant to saturation so such refrigerant will be essentially in a vapor phase for re-entry into the suction header 32 and return to the compressors without slugging.
  • the discharge line valve 15 will connect the compressor header 15 through conduit 16 to both outside condenser sections 18 and 19, and the reversing valve 21 will connect the outflow conduit 20 directly to condensate line 22 to the receiver 23.
  • the heat reclaim coil 35 is isolated from the refrigeration circuit by the reversing valves 15 and 21 and the check valve 50, and the solenoid valve 61 is opened to permit refrigerant pump out from the heat reclaim coil 35 to suction through conduit 60.
  • Condensing capacity of the condenser sections 18 and 19 is conventionally controlled by cycling zone condenser fans (not shown) or the like to remove superheat and reduce the refrigerant to a subcooled liquid phase.
  • the thermostat 52 will switch the reversing valve 15 to connect the compressor discharge header 14 into line 44 to the heat reclaim coil 35 thereby disconnecting the discharge conduit 16 leading to condenser branch conduits 18a and 19a.
  • Air circulation through the air handler 36 will effect heat exchange in the heat reclaim coil 35 in a normal manner whereby superheated refrigerant energy (upwards of 75%) is transferred to the recirculated store air and the refrigerant is thus cooled toward its saturation level.
  • the refrigerant then flows out through conduits 46 and 48 through check valve 50 into one condenser section 19 to complete final condensation to a subcooled liquid phase, and the refrigerant condensate then flows through conduit 20, valve 21 and conduit 22 to the receiver 23.
  • the outside condenser 17 effects refrigerant cooling or condensation by ambient air flow therethrough and is sized according to design entering air temperatures and heat rejection loads to meet summer requirements.
  • the condensing capacity of the outside condenser 17 greatly exceeds the winter requirements, and the split condenser 18, 19 permits one-half of the outside condenser to be disconnected from the refrigeration circuit.
  • Deep refrigerant subcooling can be inherently achieved during winter and moderate weather conditions by controlling condenser capacity, and the primary objective is to provide efficient refrigeration operation by maintaining a minimum compressor head pressure as by throttling the flooding valve 24 to backflood the condenser section 19 and reduce its effective heat exchange surface.
  • the method of operation in summer weather achieves the potential of the present invention in which the reverse operating refrigerant flow mode through the heat reclaim coil 35 effects deep subcooling and air conditioning humidity control through reheat.
  • the reversing valve 15 is positioned to deliver the compressor discharge through conduit 16 to both condenser sections 18 and 19 for maximum outdoor condensing capacity to meet design entering air temperatures and heat rejection loads.
  • the reversing valve 21 is operated in response to a second thermostatic control 62 responsive to the temperature of the building space S to connect the condensate line 20 to conduits 58, 46 and circulate refrigerant condensate in reverse cycle through the heat reclaim coil 35 and back through conduit 59 to connect through the valve 21 to condensate line 22 to the receiver 23.
  • the reversing valve 21 is preferably a slow-acting valve to permit the refrigerant condensate outflow in conduit 20 to be directed into line 58 to the coil 35 without creating a hydrostatic surge condition that might otherwise produce a hammering effect due to change of refrigerant phase in the downstream lines.
  • the typical outside condenser 17 is sized to meet the normal summer refrigeration requirements of the system evaporators 27, 28 and 29, there is little subcooling effect, if any, in the refrigerant condensate in liquid line 25 in a conventional refrigeration system.
  • the heat reclaim coil 35 is located in downstream air flow of the air conditioning coil 38 in the air handler unit 36 so that the flow of cold supply air from the coil 38 passes through the heat reclaim coil 35 in heat exchange relation with the refrigerant condensate therein.
  • the attributes of the reverse cycle refrigerant flow through the coil 35 and conditioned air heat exchange therewith are that (1) the cold conditioned air temperature is warmed or "reheated" a few degrees to a warmer temperature so that the space supply air is not at or near saturation and store air dehumidification as well as cooling is enhanced, and (2) the condensed liquid refrigerant in the heat exchange coil 35 is substantially subcooled to improve the performance of evaporators 27-29.
  • the reverse cycle summer mode of the heat reclaim coil 35 produces both air conditioning reheat and deep refrigerant subcooling without the use of separate reheat or mechanical subcooler devices presently being employed, and such subcooling results in substantial compressor energy requirements and power savings.
  • the comfort zone is considered to be an overriding factor in view of the fact that the refrigeration system components are sized to meet proper design refrigeration requirements even without reverse cycle summer deep subcooling. Therefore, the second thermostatic control 62 continually operates the heat reclaim coil 35 in its reverse cycle subcooling and reheat mode during the summer at all times the air conditioning system (40) is operational except when the comfort zone of the space S exceeds a predetermined value, such as a temperature of 75° F. and 50% RH or 79° F. and 25% RH.
  • a predetermined value such as a temperature of 75° F. and 50% RH or 79° F. and 25% RH.
  • the reversing valve 21 is switched to disconnect the heat reclaim coil 35 and discontinue subcooling in order to achieve maximum air conditioning temperatures (even at the expense of higher relative humidity levels) until the store zone S is brought back to a preselected comfort zone temperature at which time the subcooling refrigerant circuit is reestablished.
  • the present invention is also beneficial in reducing the amount of refrigerant overcharge required for year-round refrigeration system operations.
  • the state of the refrigerant varies substantially between summer and winter operation in a conventional refrigeration system. In the summer, the volume of refrigerant is substantially greater due to the typically higher refrigerant temperatures created by higher compressor head pressures and refrigerant condensation that only meets design requirements with the result that the receiver 23 is typically filled with excess refrigerant. This overcharge is required, however, during winter operation in which a denser subcooled refrigerant state is naturally achieved.
  • this refrigerant design overcharge which may range to about 250 pounds or 30%, can be substantially reduced by as much as 40% due to the split (one-half) outside condenser reduction and bleed down in the winter mode, and the use of the heat reclaim coil 35 producing deep subcooling and a solid liquid phase in the summer mode may produce an additional 10% reduction in the overcharge requirement thereby effecting substantial savings in refrigerant costs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US06/929,422 1986-11-12 1986-11-12 Reverse cycle heat reclaim coil and subcooling method Expired - Fee Related US4711094A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US06/929,422 US4711094A (en) 1986-11-12 1986-11-12 Reverse cycle heat reclaim coil and subcooling method
CA000548148A CA1274094A (fr) 1986-11-12 1987-09-29 Serpentin recuperateur de chaleur et methode de sous-refroidissement a cycle inverse
DE19873735808 DE3735808A1 (de) 1986-11-12 1987-10-22 Waermerueckgewinnungs- und unterkuehlungsanlage sowie verfahren zum erzeugen von ganzjaehriger unterkuehlung in einer kaelteanlage
GB8724996A GB2198828B (en) 1986-11-12 1987-10-26 Refrigeration system
JP62285138A JPS63140259A (ja) 1986-11-12 1987-11-11 熱再生および過冷却装置およびその方法
AU81118/87A AU583246B2 (en) 1986-11-12 1987-11-11 Reverse cycle heat reclaim coil and subcooling method
SE8704402A SE8704402L (sv) 1986-11-12 1987-11-11 Vermeatervinnings- och underkylningssystem

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US06/929,422 US4711094A (en) 1986-11-12 1986-11-12 Reverse cycle heat reclaim coil and subcooling method

Publications (1)

Publication Number Publication Date
US4711094A true US4711094A (en) 1987-12-08

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Application Number Title Priority Date Filing Date
US06/929,422 Expired - Fee Related US4711094A (en) 1986-11-12 1986-11-12 Reverse cycle heat reclaim coil and subcooling method

Country Status (7)

Country Link
US (1) US4711094A (fr)
JP (1) JPS63140259A (fr)
AU (1) AU583246B2 (fr)
CA (1) CA1274094A (fr)
DE (1) DE3735808A1 (fr)
GB (1) GB2198828B (fr)
SE (1) SE8704402L (fr)

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US5065588A (en) * 1989-08-17 1991-11-19 Hitachi, Ltd. Air-conditioner system
US5099654A (en) * 1987-02-26 1992-03-31 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co. Kg Method for controlling a motor vehicle air conditioning system
US5551249A (en) * 1992-10-05 1996-09-03 Van Steenburgh, Jr.; Leon R. Liquid chiller with bypass valves
US5651258A (en) * 1995-10-27 1997-07-29 Heat Controller, Inc. Air conditioning apparatus having subcooling and hot vapor reheat and associated methods
US5791153A (en) * 1995-11-09 1998-08-11 La Roche Industries Inc. High efficiency air conditioning system with humidity control
US5826443A (en) * 1997-12-06 1998-10-27 Ares; Roland Heat pump with heat-pipe enhancement and with primary system reheat
US5826434A (en) * 1995-11-09 1998-10-27 Novelaire Technologies, L.L.C. High efficiency outdoor air conditioning system
US6216481B1 (en) * 1999-09-15 2001-04-17 Jordan Kantchev Refrigeration system with heat reclaim and with floating condensing pressure
US6227003B1 (en) * 1999-10-22 2001-05-08 David Smolinsky Reverse-cycle heat pump system and device for improving cooling efficiency
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US6381970B1 (en) 1999-03-05 2002-05-07 American Standard International Inc. Refrigeration circuit with reheat coil
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US20050229629A1 (en) * 2002-12-16 2005-10-20 Behr Gmbh & Co. Kg Refrigerant circuit and a refrigerating system
US20060010907A1 (en) * 2004-07-15 2006-01-19 Taras Michael F Refrigerant system with tandem compressors and reheat function
US20060086115A1 (en) * 2004-10-22 2006-04-27 York International Corporation Control stability system for moist air dehumidification units and method of operation
US20060090504A1 (en) * 2004-10-28 2006-05-04 Carrier Corporation Multi-temp system with tandem compressors and reheat function
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CN103518108A (zh) * 2011-03-08 2014-01-15 绿地玛斯特Ipco有限公司 热能系统和操作方法
US20160010904A1 (en) * 2014-07-10 2016-01-14 Systèmes Lmp Inc. Transcritical r744 refrigeration system with gas cooler outlet vapors used as a heat source for the dehumidifying coil
US9322581B2 (en) 2011-02-11 2016-04-26 Johnson Controls Technology Company HVAC unit with hot gas reheat
US9360236B2 (en) 2008-06-16 2016-06-07 Greenfield Master Ipco Limited Thermal energy system and method of operation
US9556856B2 (en) 2007-07-06 2017-01-31 Greenfield Master Ipco Limited Geothermal energy system and method of operation
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US9915247B2 (en) 2007-07-06 2018-03-13 Erda Master Ipco Limited Geothermal energy system and method of operation
US10823470B2 (en) 2016-02-03 2020-11-03 Carrier Corporation Liquid accumulator for heat exchange system, refrigeration system having the same, cascade refrigeration system and control method thereof
US10928107B2 (en) 2015-06-08 2021-02-23 Danfoss A/S Method for operating a vapour compression system with heat recovery
CN112833531A (zh) * 2019-11-25 2021-05-25 青岛海尔空调电子有限公司 换热器及空调器
US11629866B2 (en) 2019-01-02 2023-04-18 Johnson Controls Tyco IP Holdings LLP Systems and methods for delayed fluid recovery
US11867437B2 (en) 2021-04-29 2024-01-09 Flo Energy Solutions Inc. HVAC dual de-superheating/subcooling heat reclaim system for transcritical refrigeration systems

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JP2908013B2 (ja) * 1990-07-31 1999-06-21 株式会社東芝 空気調和機
GB2422653B (en) * 2005-01-10 2011-03-02 Arctic Circle Ltd Refrigeration apparatus having a heating capability during cold weather
DE102010003915B4 (de) 2010-04-13 2015-11-19 WESKA Kälteanlagen GmbH Kälteanlage mit Wärmerückgewinnung und Verfahren zum Betreiben der Kälteanlage
CN106546025A (zh) * 2016-12-07 2017-03-29 珠海格力电器股份有限公司 换热系统及空调器

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US10823470B2 (en) 2016-02-03 2020-11-03 Carrier Corporation Liquid accumulator for heat exchange system, refrigeration system having the same, cascade refrigeration system and control method thereof
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SE8704402D0 (sv) 1987-11-11
GB8724996D0 (en) 1987-12-02
GB2198828A (en) 1988-06-22
AU583246B2 (en) 1989-04-20
CA1274094A (fr) 1990-09-18
AU8111887A (en) 1988-05-26
SE8704402L (sv) 1988-05-13
JPS63140259A (ja) 1988-06-11
GB2198828B (en) 1990-08-15
DE3735808A1 (de) 1988-05-26

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